US9764785B2 - Roller of track-type traveling vehicle - Google Patents

Roller of track-type traveling vehicle Download PDF

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US9764785B2
US9764785B2 US14/362,649 US201414362649A US9764785B2 US 9764785 B2 US9764785 B2 US 9764785B2 US 201414362649 A US201414362649 A US 201414362649A US 9764785 B2 US9764785 B2 US 9764785B2
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sliding bearing
roller
thrust sliding
track
contact
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US20150274228A1 (en
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Naoaki Kita
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Komatsu Ltd
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Komatsu Ltd
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/08—Endless track units; Parts thereof
    • B62D55/14—Arrangement, location, or adaptation of rollers
    • B62D55/15—Mounting devices, e.g. bushings, axles, bearings, sealings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/08—Endless track units; Parts thereof
    • B62D55/14—Arrangement, location, or adaptation of rollers

Definitions

  • the present invention relates to a roller of a track-type traveling vehicle.
  • a track-type traveling vehicle such as a hydraulic excavator, a bulldozer, and the like has been used for a work on an uneven terrain.
  • the track-type traveling vehicle includes an idler tumbler and a drive wheel arranged at front and back positions on each of both right and left sides of a traveling body, and an endless crawler belt wound around between the drive wheel and the idler tumbler.
  • On a ground non-engaging surface side of the crawler belt a plurality of rollers are arranged between the drive wheel and the idler tumbler. Since the plurality of rollers are provided, a ground engaging force during traveling of the track-type traveling vehicle can be ensured, and the vehicle body can be stably supported.
  • a roller shell which abuts a crawler belt link is rotatably provided to an outer circumference of a columnar shaft.
  • a bushing is provided between the roller shell and the shaft. The bushing has a columnar portion which receives a load in a radial direction, and a flange portion which receives a load in a thrust direction.
  • PTD 1 Japanese Patent Laying-Open No. 9-226644
  • the bushing having the columnar portion and the flange portion in an integral manner is provided, and when a roller rotates, the flange portion slides with respect to a boss portion.
  • the bushing is configured to have a columnar portion and a flange portion provided separately, when a roller rotates, the flange portion also rotates in association with the rotation of the roller, and the flange portion and the roller slide.
  • the flange portion and the roller slide with a high contact pressure, and thereby heat is generated due to frictional resistance. This heat generation results in occurrence of seizure and a reduced life of the bushing.
  • the present invention has been made in view of the aforementioned problem, and one object of the present invention is to provide a roller of a track-type traveling vehicle in which a bearing supporting a roller shell has an improved sliding abrasion resistance.
  • a roller of a track-type traveling vehicle in accordance with the present invention includes a shaft, a roller shell, a collar, a radial sliding bearing, and a thrust sliding bearing.
  • the shaft has a cylindrical outer circumferential surface.
  • the roller shell is arranged to surround a portion of the outer circumferential surface in a circumferential direction.
  • the roller shell has a cylindrical inner circumferential surface which faces the outer circumferential surface, and an annular end surface.
  • the collar is fixed to the shaft.
  • the collar has an annular facing surface which faces the end surface.
  • the radial sliding bearing is arranged between the outer circumferential surface and the inner circumferential surface.
  • the thrust sliding bearing is arranged between the end surface and the facing surface.
  • the thrust sliding bearing is provided separately from the radial sliding bearing.
  • the roller is provided with an anti-rotation structure. The anti-rotation structure prevents relative rotation of the thrust sliding bearing with respect to the roller shell.
  • the roller in accordance with the present invention relative rotation of the thrust sliding bearing, which is provided separately from the radial sliding bearing, with respect to the roller shell is prevented.
  • the thrust sliding bearing does not slide with respect to the roller shell, and slides with respect to the collar. Since an area in which the thrust sliding bearing is in contact with the collar is larger than an area in which the thrust sliding bearing is in contact with the roller shell, contact pressure generated during sliding can be reduced by sliding the thrust sliding bearing with respect to the collar. As a result, heat generation during the sliding of the thrust sliding bearing supporting the roller shell can be reduced.
  • the outer circumferential surface of the shaft has a shape of a cylinder with an identical diameter from a position where the end surface is arranged to a position where the facing surface is arranged, in an axial direction.
  • the outer circumferential surface of the shaft is not provided with a step difference for receiving a thrust load, at a position where the thrust sliding bearing is provided, and the shaft has a shape of a straight shaft having an outer circumferential surface in the shape of a cylinder with an identical diameter.
  • the anti-rotation structure is joining by engagement between a convex portion formed in one of the roller shell and the thrust sliding bearing and a concave portion formed in the other of the roller shell and the thrust sliding bearing.
  • the radial sliding bearing and the thrust sliding bearing are formed of materials different from each other.
  • the thrust sliding bearing sliding with a relatively high contact pressure can be formed of a material which is resistant to a high contact pressure, and thus the thrust sliding bearing can have a further longer life.
  • the material forming the thrust sliding bearing has a hardness higher than that of the material forming the radial sliding bearing. With this configuration, the thrust sliding bearing can be provided to be resistant to a higher contact pressure.
  • the thrust sliding bearing has an annular plate-shaped body portion having an annular main surface, and a convex portion formed integrally with the body portion and protruding from the main surface.
  • an area in which the thrust sliding bearing is in contact with the end surface of the roller shell is smaller than an area in which the thrust sliding bearing is in contact with the facing surface of the collar.
  • a dimension of a portion in which the thrust sliding bearing is in contact with the end surface of the roller shell is smaller than a dimension of a portion in which the thrust sliding bearing is in contact with the facing surface of the collar.
  • the bearing supporting the roller shell can have an improved sliding abrasion resistance.
  • FIG. 1 is a schematic perspective view showing a configuration of a hydraulic excavator as an example of a track-type traveling vehicle having a roller in one embodiment of the present invention.
  • FIG. 2 is a schematic perspective view showing a configuration of a crawler belt device included in the track-type traveling vehicle of FIG. 1 .
  • FIG. 3 is a cross sectional view showing a schematic configuration of a track roller of the track-type traveling vehicle in accordance with one embodiment of the present invention.
  • FIG. 4 is a cross sectional view showing the vicinity of a thrust sliding bearing shown in FIG. 3 in an enlarged manner.
  • FIG. 5 is an exploded perspective view of some of components of the track roller shown in FIG. 3 .
  • FIG. 6 is a perspective view of the thrust sliding bearing.
  • FIG. 7 is a cross sectional view showing details of arrangement of the thrust sliding bearing with respect to a roller shell and a collar.
  • FIG. 1 is a schematic perspective view showing a configuration of a hydraulic excavator as an example of a track-type traveling vehicle having a roller in one embodiment of the present invention.
  • a track-type traveling vehicle (for example, hydraulic excavator) 30 mainly has a travel base structure 20 , a revolving superstructure 31 , and a work implement 32 .
  • Travel base structure 20 and revolving superstructure 31 constitute a main body of the track-type traveling vehicle.
  • Travel base structure 20 has a pair of right and left crawler belt devices 10 .
  • Track-type traveling vehicle 30 is configured to self-propel by rotationally driving the pair of right and left crawler belt devices 10 .
  • Travel base structure 20 also has a roller which will be described later in detail.
  • Revolving superstructure 31 is mounted revolvably with respect to travel base structure 20 .
  • Revolving superstructure 31 has a cab 31 a on a front left side, and has an engine compartment 31 b accommodating an engine and a counterweight 31 c on a back side.
  • the front and back/right and left of revolving superstructure 31 are defined with respect to an operator sitting in cab 31 a.
  • Work implement 32 is pivotally supported on the front side of revolving superstructure 31 , and has, for example, a boom, an arm, a bucket, hydraulic cylinders, and the like.
  • FIG. 2 is a schematic perspective view showing a configuration of crawler belt device 10 included in the track-type traveling vehicle of FIG. 1 .
  • crawler belt device 10 mainly has a crawler belt link 1 , a bushing 11 , a coupling pin 12 , and a track shoe plate (shoe plate) 13 .
  • Crawler belt device 10 is configured in a looped shape by coupling, in an endless manner, a plurality of crawler belt links 1 having track shoe plates 13 attached thereto.
  • a bushing hole 6 and a pin hole 7 are formed in crawler belt link 1 .
  • the plurality of crawler belt links 1 are arranged in two rows.
  • One crawler belt link 1 and the other crawler belt link 1 located adjacent to each other in the same row are overlapped with each other such that bushing hole 6 of one crawler belt link 1 and pin hole 7 of the other crawler belt link 1 are arranged concentrically.
  • Cylindrical bushing 11 is press-fit into bushing hole 6 of one crawler belt link 1 .
  • Coupling pin 12 is inserted into bushing 11 , and press-fit into pin hole 7 of the other crawler belt link 1 . Thereby, one crawler belt link 1 and the other crawler belt link 1 arranged in the row direction are coupled to each other.
  • bushing hole 6 of crawler belt link 1 in the first row and pin hole 7 of crawler belt link 1 in the second row are arranged to be concentric to each other.
  • Crawler belt link 1 in the first row is placed on one end side of one bushing 11 and coupling pin 12 as described above, and crawler belt link 1 in the second row is placed on the other end side thereof.
  • crawler belt links 1 in one row and the other row are coupled to each other, using bushing 11 and coupling pin 12 .
  • Track shoe plate 13 has a ground engaging surface 13 a on a side in contact with the ground, and a ground non-engaging surface 13 b opposite to ground engaging surface 13 a .
  • Ground engaging surfaces 13 a of a plurality of track shoe plates 13 constitute a ground engaging surface of crawler belt device 10 .
  • Ground non-engaging surfaces 13 b of the plurality of track shoe plates 13 constitute a ground non-engaging surface of crawler belt device 10 .
  • a track roller 21 as an example of a roller in accordance with the present embodiment is arranged on the ground non-engaging surface side of endless crawler belt device 10 , and rotates in contact with crawler belt links 1 .
  • Track roller 21 is provided at a lower portion of a track frame 29 (see FIG. 1 ) of travel base structure 20 to guide rotation of crawler belt device 10 via crawler belt links 1 .
  • Track roller 21 includes a shaft 24 fixed to track frame 29 , and a roller shell 23 which abuts crawler belt links 1 .
  • FIG. 3 is a cross sectional view showing a schematic configuration of track roller 21 of the track-type traveling vehicle in accordance with one embodiment of the present invention.
  • shaft 24 is attached to track frame 29 .
  • Shaft 24 is formed in the shape of a substantially solid column, and has a cylindrical outer circumferential surface 24 a.
  • Roller shell 23 is arranged to surround a portion of outer circumferential surface 24 a of shaft 24 in a circumferential direction. Roller shell 23 is arranged on the outer circumferential side of shaft 24 to be rotatable about the center line of shaft 24 . Roller shell 23 has a tubular shape. Roller shell 23 is produced by welding two segments separated at a radial plane including the center of the direction of the center line described above. Shaft 24 is inserted in tubular roller shell 23 , and serves as the center of rotation of roller shell 23 . Roller shell 23 has a cylindrical inner circumferential surface 23 a which faces outer circumferential surface 24 a of shaft 24 along a direction of the center of rotation (axial direction), and an annular end surface 23 b along a radial direction.
  • a pair of collars 22 are provided on both end sides of shaft 24 with respect to roller shell 23 .
  • Collars 22 are arranged to sandwich roller shell 23 therebetween in the axial direction.
  • Each collar 22 has a tubular shape, and is attached to shaft 24 such that shaft 24 is inserted in a central portion thereof.
  • Collar 22 is fixed to shaft 24 using a pin 28 .
  • a floating seal 27 is arranged between collar 22 and roller shell 23 .
  • Collar 22 has an annular facing surface 22 b .
  • Collar 22 and roller shell 23 are arranged such that facing surface 22 b of collar 22 faces end surface 23 b of roller shell 23 .
  • a radial sliding bearing 25 is arranged between outer circumferential surface 24 a of shaft 24 and inner circumferential surface 23 a of roller shell 23 .
  • Radial sliding bearing 25 is provided to receive a load in a radial direction (radial direction of shaft 24 ) and allow relative rotation of roller shell 23 with respect to shaft 24 .
  • a thrust sliding bearing 26 is arranged between end surface 23 b of roller shell 23 and facing surface 22 b of collar 22 .
  • Thrust sliding bearing 26 is provided to receive a load in a thrust direction (axial direction of shaft 24 ) and allow relative rotation of roller shell 23 with respect to collar 22 .
  • Radial sliding bearing 25 and thrust sliding bearing 26 support roller shell 23 in the radial direction and the axial direction such that roller shell 23 is relatively rotatable with respect to shaft 24 and collar 22 , respectively.
  • Radial sliding bearing 25 is press fit into inner circumferential surface 23 a of roller shell 23 , and provided to be rotatable integrally with roller shell 23 .
  • Thrust sliding bearing 26 is arranged, with respect to roller shell 23 , on a side facing collar 22 in the axial direction.
  • FIG. 4 is a cross sectional view showing the vicinity of thrust sliding bearing 26 shown in FIG. 3 in an enlarged manner.
  • one of thrust surfaces of thrust sliding bearing 26 is arranged at a position substantially identical to the position of end surface 23 b of roller shell 23 in the axial direction of shaft 24 (right-and-left direction in the drawing).
  • the other of the thrust surfaces of thrust sliding bearing 26 is arranged at a position substantially identical to the position of facing surface 22 b of collar 22 in the axial direction of shaft 24 .
  • a gap G is formed between thrust sliding bearing 26 and radial sliding bearing 25 .
  • Radial sliding bearing 25 and thrust sliding bearing 26 are arranged so as not to contact with each other.
  • Radial sliding bearing 25 and thrust sliding bearing 26 are provided as separate members completely separated by gap G.
  • hollow cylindrical radial sliding bearing 25 is arranged between outer circumferential surface 24 a of shaft 24 and inner circumferential surface 23 a of roller shell 23 .
  • Annular plate-shaped thrust sliding bearing 26 has an inner circumferential end surface with a diameter substantially identical to an outer diameter of shaft 24 .
  • Thrust sliding bearing 26 has an outer circumferential end surface located at a position which is radially outward with respect to outer circumferential surface 24 a of shaft 24 and is away from outer circumferential surface 24 a.
  • Collar 22 is arranged from outer circumferential surface 24 a of shaft 24 to the outer circumferential end surface of thrust sliding bearing 26 in the radial direction of shaft 24 . Facing surface 22 b of collar 22 is provided to face a substantially entire surface of one thrust surface of thrust sliding bearing 26 (on the left side in FIG. 4 ). Since radial sliding bearing 25 is arranged between shaft 24 and roller shell 23 , end surface 23 b of roller shell 23 is provided to face only a radially outward portion of the other thrust surface of thrust sliding bearing 26 . That is, of the other thrust surface of thrust sliding bearing 26 (on the right side in FIG. 4 ), a portion in the vicinity of the inner circumferential end surface of thrust sliding bearing 26 is arranged at a position not facing end surface 23 b of roller shell 23 .
  • Outer circumferential surface 24 a of shaft 24 has a shape of a cylinder with an identical diameter from a position where end surface 23 b of roller shell 23 is arranged to a position where facing surface 22 b of collar 22 is arranged, in the axial direction of shaft 24 .
  • Outer circumferential surface 24 a of shaft 24 is not provided with a step difference for receiving a thrust load, at a portion spanning thrust sliding bearing 26 in the axial direction, and shaft 24 has a shape of a straight shaft having cylindrical outer circumferential surface 24 a.
  • Radial sliding bearing 25 and thrust sliding bearing 26 provided separately are formed of materials different from each other.
  • the material forming thrust sliding bearing 26 has a hardness higher than that of the material forming radial sliding bearing 25 .
  • a material having a Brinell hardness double or more that of the material forming radial sliding bearing 25 may be applied.
  • a material having a Brinell hardness of 200 or more may be selected as the material forming thrust sliding bearing 26 .
  • a lead bronze casting such as CAC603 specified by BS (Japanese Industrial Standards) H 5120 may be applied.
  • a high-strength brass casting Cu—Zn—Mn—Fe—Al-based alloy having more excellent mechanical properties such as CAC301, CAC302, CAC303, or CAC304 specified by JIS H 5120 may be applied.
  • FIG. 5 is an exploded perspective view of some of the components of track roller 21 shown in FIG. 3 .
  • FIG. 6 is a perspective view of thrust sliding bearing 26 .
  • thrust sliding bearing 26 is provided separately from radial sliding bearing 25 .
  • Thrust sliding bearing 26 has an annular plate-shaped body portion 26 m .
  • Body portion 26 m has annular main surfaces 26 t on one side and the other side in the direction of the center of rotation.
  • Main surface 26 t on one side faces end surface 23 b of roller shell 23
  • main surface 26 t on the other side faces facing surface 22 b of collar 22 .
  • Main surfaces 26 t have a function as the thrust surfaces receiving a thrust force between roller shell 23 and collar 22 .
  • Thrust sliding bearing 26 further has convex portions 26 p protruding from main surface 26 t on one side of body portion 26 m .
  • Convex portions 26 p are provided in main surface 26 t at two positions.
  • Convex portions 26 p extend in the radial direction of annular main surface 26 t , and are formed from the inner circumferential end surface to the outer circumferential end surface of thrust sliding bearing 26 .
  • Convex portions 26 p at two positions are formed such that they extend in a direction which is on an identical straight line passing through the center of annular main surface 26 t.
  • Convex portion 26 p is formed integrally with body portion 26 m .
  • Such thrust sliding bearing 26 can be easily formed by molding the material by casting and further cutting the material for shaping.
  • Convex portion 26 p may be formed to protrude from main surface 26 t to the same extent as the thickness of body portion 26 m .
  • a distance between a leading end of convex portion 26 p and main surface 26 t from which convex portion 26 p protrudes in a thickness direction of thrust sliding bearing 26 may also be set to 3.5 mm.
  • concave portions 23 c where portions of end surface 23 b are recessed are formed. Each concave portion 23 c is configured to be able to accommodate convex portion 26 p therein.
  • Concave portions 23 c are formed in annular end surface 23 b of roller shell 23 at two positions, and formed to extend in the radial direction of end surface 23 b . Concave portions 23 c at two positions are formed such that they extend in a direction which is on an identical straight line passing through the center of annular end surface 23 b .
  • the shape of concave portion 23 c is determined corresponding to the shape of convex portion 26 p .
  • Convex portion 26 p and concave portion 23 c are formed such that convex portion 26 p fits in concave portion 23 c with no space therebetween, or with a minute space between a surface of convex portion 26 p and an inner surface of concave portion 23 c.
  • convex portions 26 p formed in thrust sliding bearing 26 engage concave portions 23 c formed in roller shell 23 , when roller shell 23 rotates, thrust sliding bearing 26 rotates together with roller shell 23 .
  • Engagement between convex portions 26 p and concave portions 23 c has a function as an anti-rotation structure which prevents relative rotation of thrust sliding bearing 26 with respect to roller shell 23 .
  • the number of convex portions 26 p and concave portions 23 c may be any number. From the viewpoints of decreasing the material forming thrust sliding bearing 26 and fully exercising the function of preventing rotation of thrust sliding bearing 26 with respect to roller shell 23 , it is desirable to form two convex portions 26 p and two concave portions 23 c as described above.
  • FIG. 7 is a cross sectional view showing details of arrangement of thrust sliding bearing 26 with respect to roller shell 23 and collar 22 .
  • One of main surfaces 26 t of thrust sliding bearing 26 which function as the thrust surfaces (on the right side in FIG. 7 ) is arranged to face end surface 23 b of roller shell 23 .
  • a radial dimension R 1 shown in FIG. 7 indicates a dimension of a portion of main surface 26 t which is in contact with end surface 23 b of roller shell 23 , in the radial direction.
  • the other of main surfaces 26 t (on the left side in FIG. 7 ) is arranged to face facing surface 22 b of collar 22 .
  • a radial dimension R 2 shown in FIG. 7 indicates a dimension of a portion of main surface 26 t which is in contact with facing surface 22 b of collar 22 , in the radial direction.
  • radial dimension R 1 is smaller than radial dimension R 2 . That is, a relational expression R 1 ⁇ R 2 is established.
  • an area in which one main surface 26 t of thrust sliding bearing 26 is in contact with end surface 23 b of roller shell 23 is smaller than an area in which the other main surface 26 t is in contact with facing surface 22 b of collar 22 .
  • thrust sliding bearing 26 arranged between end surface 23 b of roller shell 23 and facing surface 22 b of collar 22 is provided separately from radial sliding bearing 25 .
  • Track roller 21 is provided with an anti-rotation structure which prevents relative rotation of thrust sliding bearing 26 with respect to roller shell 23 .
  • thrust sliding bearing 26 When thrust sliding bearing 26 is provided as a member separate from radial sliding bearing 25 , thrust sliding bearing 26 slides with respect to either one of end surface 23 b and facing surface 22 b to support roller shell 23 to be relatively rotatable with respect to collar 22 . Since the area in which thrust sliding bearing 26 is in contact with collar 22 is larger than the area in which thrust sliding bearing 26 is in contact with roller shell 23 as described with reference to FIG. 7 , contact pressure generated during sliding can be reduced by sliding thrust sliding bearing 26 with respect to collar 22 .
  • thrust sliding bearing 26 does not slide with respect to roller shell 23 , and slides with respect to collar 22 .
  • contact pressure acting during the sliding of thrust sliding bearing 26 is reduced, and as a result, heat generation during the sliding can be reduced. Accordingly, occurrence of seizure of thrust sliding bearing 26 can be suppressed.
  • reduction of the diameter of track roller 21 may be considered for the purpose of avoiding interference between track roller 21 and track frame 29 , and the like.
  • the diameter of track roller 21 is reduced, the area in which thrust sliding bearing 26 is in contact with collar 22 is reduced, and thus contact pressure acting on thrust sliding bearing 26 is increased.
  • contact pressure generated during the sliding of thrust sliding bearing 26 can be reduced. That is, the configuration of the present embodiment can be applied particularly advantageously in a case where it is intended to reduce the diameter of the roller.
  • outer circumferential surface 24 a of shaft 24 has a shape of a cylinder with an identical diameter from the position where end surface 23 b of roller shell 23 is arranged to the position where facing surface 22 b of collar 22 is arranged, in the axial direction of shaft 24 .
  • outer circumferential surface 24 a of shaft 24 is not provided with a step difference for receiving a thrust load, at a position where thrust sliding bearing 26 is provided in the axial direction of shaft 24
  • shaft 24 has a shape of a straight shaft having an outer circumferential surface in the shape of a cylinder with an identical diameter.
  • the anti-rotation structure is configured by the engagement between concave portions 23 c formed in roller shell 23 and convex portions 26 p formed in thrust sliding bearing 26 .
  • the anti-rotation structure can be formed with a simple structure.
  • radial sliding bearing 25 and thrust sliding bearing 26 are formed of materials different from each other.
  • thrust sliding bearing 26 sliding with a relatively high contact pressure can be formed of a material which is resistant to a high contact pressure, such as a high-strength brass casting, and thus thrust sliding bearing 26 can have a further longer life.
  • thrust sliding bearing 26 has a hardness higher than that of the material forming radial sliding bearing 25 .
  • thrust sliding bearing 26 may be formed of a high-strength brass casting, and radial sliding bearing 25 may be formed of a lead bronze casting. With this configuration, thrust sliding bearing 26 can be provided to be resistant to a higher contact pressure.
  • thrust sliding bearing 26 has annular plate-shaped body portion 26 m having annular main surfaces 26 t , and convex portions 26 p formed integrally with body portion 26 m and protruding from main surface 26 t .
  • rotation of thrust sliding bearing 26 with respect to roller shell 23 can be prevented reliably by the engagement between convex portions 26 p formed in thrust sliding bearing 26 and concave portions 23 c formed in roller shell 23 .
  • the area in which thrust sliding bearing 26 is in contact with end surface 23 b of roller shell 23 is smaller than the area in which thrust sliding bearing 26 is in contact with facing surface 22 b of collar 22 .
  • radial dimension R 1 of a portion in which thrust sliding bearing 26 is in contact with end surface 23 b of roller shell 23 is smaller than radial dimension R 2 of a portion in which thrust sliding bearing 26 is in contact with facing surface 22 b of collar 22 .
  • the above description has described an example in which the anti-rotation structure which prevents relative rotation of thrust sliding bearing 26 with respect to roller shell 23 is configured by the engagement between convex portions 26 p formed in thrust sliding bearing 26 and concave portions 23 c formed in roller shell 23 .
  • the anti-rotation structure is not limited thereto.
  • the anti-rotation structure may be configured by joining of roller shell 23 and thrust sliding bearing 26 by any of brazing, adhesion, and welding.
  • nickel may be underlaid on end surface 23 b of roller shell 23
  • an annular plate member of a high-strength brass casting may be joined to end surface 23 b by gas tungsten arc welding, to form thrust sliding bearing 26 .
  • end surface 23 b of roller shell 23 may be treated with zinc phosphate/chromate, an annular plate member of a high-strength brass casting may be treated with an aqueous solution of nitric acid, and the plate member may be joined to roller shell 23 with an epoxy adhesive, to form thrust sliding bearing 26 .
  • a groove for a brazing filler metal may be provided in end surface 23 b of roller shell 23 , and an annular plate member of a high-strength brass casting may be brazed with brass brazing filler metal.
  • concave portions and the convex portions may be reversed to form concave portions in thrust sliding bearing 26 and form convex portions in roller shell 23 .
  • concave portions receiving convex portions 26 p may be formed in radial sliding bearing 25 .
  • the concave portions may be formed on an extension of concave portions 23 c formed in roller shell 23 in the radial direction of shaft 24 .
  • Shaft 24 is not limited to a cylindrical straight shaft as shown in FIG. 3 , and a stepped shaft with a step difference in a shape whose diameter is reduced toward an end portion may also be applied.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Rolling Contact Bearings (AREA)
US14/362,649 2013-06-17 2014-02-27 Roller of track-type traveling vehicle Active 2034-10-29 US9764785B2 (en)

Applications Claiming Priority (3)

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JP2013126347A JP5552558B1 (ja) 2013-06-17 2013-06-17 履帯式走行車両の転輪
JP2013-126347 2013-06-17
PCT/JP2014/054867 WO2014203563A1 (ja) 2013-06-17 2014-02-27 履帯式走行車両の転輪

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US9764785B2 true US9764785B2 (en) 2017-09-19

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JP (1) JP5552558B1 (ja)
KR (1) KR101750637B1 (ja)
DE (1) DE112014000234B4 (ja)
IN (1) IN2015DN04014A (ja)
WO (1) WO2014203563A1 (ja)

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US20220227437A1 (en) * 2021-01-21 2022-07-21 Caterpillar Inc. Rim for a track roller

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WO2019198111A1 (en) * 2018-04-13 2019-10-17 Italtractor Itm S.P.A. Element of a crawler-track movement assembly for works vehicles
US11654983B2 (en) * 2019-06-10 2023-05-23 Caterpillar Inc. Rotatable element in machine track having thrust washer stack for stepping down relative speeds
KR20220032742A (ko) 2020-09-08 2022-03-15 엘지디스플레이 주식회사 표시 장치
US11724757B2 (en) * 2020-10-29 2023-08-15 Caterpillar Inc. Roller frame assembly in ground-engaging track system having anti-backbending rollers and method
JP7494763B2 (ja) * 2021-02-26 2024-06-04 株式会社豊田自動織機 流体機械

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US20220227437A1 (en) * 2021-01-21 2022-07-21 Caterpillar Inc. Rim for a track roller
US11987302B2 (en) * 2021-01-21 2024-05-21 Caterpillar Inc. Rim for a track roller

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IN2015DN04014A (ja) 2015-06-26
US20150274228A1 (en) 2015-10-01
KR101750637B1 (ko) 2017-06-23
KR20150068467A (ko) 2015-06-19
DE112014000234B4 (de) 2018-11-08
JP5552558B1 (ja) 2014-07-16
WO2014203563A1 (ja) 2014-12-24
JP2015000666A (ja) 2015-01-05

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